WO2018038818A1 - Refrigerant compressor - Google Patents

Refrigerant compressor Download PDF

Info

Publication number
WO2018038818A1
WO2018038818A1 PCT/US2017/042055 US2017042055W WO2018038818A1 WO 2018038818 A1 WO2018038818 A1 WO 2018038818A1 US 2017042055 W US2017042055 W US 2017042055W WO 2018038818 A1 WO2018038818 A1 WO 2018038818A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant compressor
axial
centrifugal
compressor
refrigerant
Prior art date
Application number
PCT/US2017/042055
Other languages
French (fr)
Inventor
Justin Jongsik OH
Original Assignee
Danfoss A/S
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to US201662379367P priority Critical
Priority to US62/379,367 priority
Application filed by Danfoss A/S filed Critical Danfoss A/S
Publication of WO2018038818A1 publication Critical patent/WO2018038818A1/en

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08Centrifugal pumps
    • F04D17/10Centrifugal pumps for compressing or evacuating
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01DNON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00Regulating or controlling by varying flow
    • F01D17/10Final actuators
    • F01D17/12Final actuators arranged in stator parts
    • F01D17/14Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/16Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes
    • F01D17/162Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes for axial flow, i.e. the vanes turning around axes which are essentially perpendicular to the rotor centre line
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/02Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
    • F04D17/025Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal comprising axial flow and radial flow stages
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00Axial-flow pumps
    • F04D19/02Multi-stage pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/40Casings; Connections of working fluid
    • F04D29/52Casings; Connections of working fluid for axial pumps
    • F04D29/54Fluid-guiding means, e.g. diffusers
    • F04D29/56Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/563Fluid-guiding means, e.g. diffusers adjustable specially adapted for elastic fluid pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/66Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
    • F04D29/684Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps by fluid injection
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B1/00Compression machines, plant, or systems with non-reversible cycle
    • F25B1/04Compression machines, plant, or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053Compression machines, plant, or systems with non-reversible cycle with compressor of rotary type of turbine type
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/26Rotors specially for elastic fluids
    • F04D29/28Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05DINDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2210/00Working fluids
    • F05D2210/10Kind or type
    • F05D2210/14Refrigerants with particular properties, e.g. HFC
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05DINDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00Components
    • F05D2240/10Stators
    • F05D2240/12Fluid guiding means, e.g. vanes
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05DINDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00Geometry
    • F05D2250/50Inlet or outlet
    • F05D2250/51Inlet

Abstract

One exemplary embodiment of this disclosure relates to a refrigerant compressor. The compressor includes an axial section having a plurality of blades and vanes and a centrifugal section having an impeller. The centrifugal section is arranged downstream of the axial section.

Description

REFRIGERANT COMPRESSOR
RELATED APPLICATIONS
[0001] This application claims the benefit of U.S. Provisional Application No. 62/379,367, filed August 25, 2016, which is herein incorporated by reference in its entirety.
BACKGROUND
[0001] This disclosure relates to a compressor, such as for use in refrigeration.
[0002] Refrigerant compressors are used to circulate refrigerant in a chiller via a refrigerant loop. Refrigerant loops are known to include a condenser, an expansion device, and an evaporator. The compressor compresses the fluid, which then travels to a condenser, which cools and condenses the fluid. The refrigerant then goes to an expansion device, which decreases the pressure of the fluid, and to the evaporator, where the fluid is vaporized, completing a refrigeration cycle.
[0003] Environmental regulations have led to refrigerants with lower working pressure being preferred in minimizing the global warming potential and the ozone depletion potential. These lower working pressure refrigerants have a lower vapor density than higher working pressure refrigerants, requiring a larger cross-section area in order to pass the same mass flow rate. This larger cross-section area leads to bigger machine sizes and lower shaft speeds than machines that use higher working pressure refrigerants.
SUMMARY
[0004] An example refrigerant compressor according to an exemplary aspect of this disclosure includes an axial section having a plurality of blades and vanes and a centrifugal or mixed-flow section having an impeller. The centrifugal or mixed-flow section is positioned downstream of the axial section.
[0005] In a further embodiment of the foregoing system, a flash vapor port is arranged upstream of the centrifugal section.
[0006] In a further embodiment of the foregoing system, an inlet guide vane is arranged upstream of the axial section.
[0007] In a further embodiment of the foregoing system, an inlet guide vane is arranged upstream of the centrifugal flow section and downstream of the axial section.
[0008] In a further embodiment of the foregoing system, the inlet guide vane is a variable inlet guide vane.
[0009] In a further embodiment of the foregoing system, a first inlet guide vane is arranged upstream of the axial section and a second inlet guide vane is arranged downstream of the axial section.
[0010] In a further embodiment of the foregoing system, a diffuser is arranged downstream of the centrifugal section.
[0011] In a further embodiment of the foregoing system, the refrigerant compressor is part of a chiller system.
[0012] In a further embodiment of the foregoing system, a flow path for a working fluid is defined by a hub and a casing.
[0013] In a further embodiment of the foregoing system, the working fluid is one of HFO-1233ZD, R123, DR-2, and HFO-1336MZZ.
[0014] In a further embodiment of the foregoing system, a deswirler row having a plurality of blades is arranged upstream of the centrifugal section.
[0015] An example refrigerant compressor according to an exemplary aspect of this disclosure includes an axial portion and a centrifugal portion arranged about an axis of rotation, and a fluid flowpath. The fluid flowpath is substantially parallel to the axis of rotation at the axial portion, and the fluid flowpath is substantially perpendicular to the axis of rotation at a portion of the centrifugal portion.
[0016] In a further embodiment of the foregoing system, the axial portion comprises a plurality of blades and a plurality of vanes, and the centrifugal portion comprises an impeller [0017] In a further embodiment of the foregoing system, the centrifugal portion comprises a diffuser, and the fluid exits the flowpath via a volute.
[0018] In a further embodiment of the foregoing system, the fluid is a refrigerant.
[0019] In a further embodiment of the foregoing system, the refrigerant is one of HFO-1233ZD, R123, DR-2, and HFO-1336MZZ.
[0020] In a further embodiment of the foregoing system, a flash vapor port is arranged upstream of the centrifugal section.
[0021] In a further embodiment of the foregoing system, the compressor includes inlet guide vanes.
[0022] The embodiments, examples and alternatives of the preceding paragraphs, the claims, or the following description and drawings, including any of their various aspects or respective individual features, may be taken independently or in any combination. Features described in connection with one embodiment are applicable to all embodiments, unless such features are incompatible.
BRIEF DESCRIPTION OF THE DRAWINGS
[0023] The drawings can be briefly described as follows:
[0024] Fii *ure 1 shows a schematic illustration of a refrigerant loop.
[0025] Fii *ure 2 shows a refrigerant compressor.
[0026] Fi. *ure 3 shows another embodiment of a refrigerant compressor.
[0027] Fii *ure 4 shows another embodiment of a refrigerant compressor.
[0028] Fii *ure 5 shows another embodiment of a refrigerant compressor.
[0029] Fii *ure 6 shows another embodiment of a refrigerant compressor.
[0030] Fii *ure 7 shows another embodiment of a refrigerant compressor.
DETAILED DESCRIPTION
[0031] Figure 1 illustrates a refrigerant cooling system 10. The refrigerant system 10 includes a main refrigerant loop, or circuit, 12 in communication with a compressor 14, a condenser 16, an evaporator 18, and an expansion device 20. This refrigerant system 10 may be used in a chiller, for example. Notably, while a particular example of the refrigerant system 10 is shown, this application extends to other refrigerant system configurations. For instance, the main refrigerant loop 12 can include an economizer downstream of the condenser 16 and upstream of the expansion device 20. [0032] The refrigerant cooling system 10 circulates a refrigerant. Increasingly, refrigerants with lower working pressure are preferred for environmentally-friendly reasons. Lower working pressure refrigerants also offer benefits in system efficiency, flammability, and toxicity. A lower working pressure refrigerant has a lower vapor pressure level, lower saturation pressure, and lower density than traditional refrigerants, such as HFC- 134a or HFO- 1234ZE. Lower working pressure refrigerants consequently require higher volumetric flow. Examples of such lower working pressure refrigerants include R123, HFO-1233ZD, HFO- 1336MZZ, and DR-2. In an embodiment, lower working pressure refrigerants have a saturation vapor pressure below 100 kilopascals (kPa) (or about 14.5 psia) at 4.4 degrees Celsius (or about 40 degrees Fahrenheit). In another embodiment, lower working pressure refrigerants include refrigerants with a liquid phase saturation pressure below 45 pounds per square inch absolute (psia) (or about 310 kPa) at 104 degrees Fahrenheit (40 degrees Celsius), as defined by the Environmental Protection Agency's Refrigerant Recycling Regulations.
[0033] Figure 2 illustrates an example refrigerant compressor 14 for a lower working pressure refrigerant. In this example, the compressor 14 includes an axial compressor section 19 and a centrifugal compressor section 21 arranged about an axis of rotation X. A fluid flow path F is bounded by a hub 22 at an interior and a shroud or casing 24 at an exterior. An inlet 25 of the compressor 14 receives fluid F from the evaporator 18. At the inlet 25, the fluid is flowing substantially parallel to the axis of rotation X. In this example, a first stage of the compressor 14 is a single-stage axial-flow section 19. The single-stage axial-flow section 19 includes a rotor row 28 having an array of rotor blades, and a stator row 30 having an array of stator vanes. The blades of the rotor row 28 are configured to provide a desired compression ratio. In an embodiment, the blades could include tip treatments, such as shrouds to help manage blade tip performance loss. The rotor row 28 elevates vapor enthalpy.
[0034] The stator row 30 elevates vapor static pressure and changes vapor swirl. The vanes of the stator row 30 are configured to remove the angular flow component imparted by the blades of the rotor row 28, and restore the axial flow direction as the working fluid F is directed downstream within the compressor 14. In one embodiment, the stator vanes may be stationary. In another embodiment, the stator row 30 may be radially adjusted, allowing for smooth transition of flow path F from the axial-flow section 19 without conventional return channel vanes. Together, the rotor row 28 and stator row 30 provide a single compression stage. It should be understood, however, that this disclosure extends to compressors having additional, or fewer, stages in the axial-flow compressor. [0035] A centrifugal section 21 is arranged downstream of the axial-flow section 19 for second stage vapor compression. The centrifugal section 21 includes a centrifugal impeller 34. In an embodiment, the fluid flows radially outwardly at the centrifugal section 21. In other words, the fluid F flows substantially perpendicular to the axis X at a portion of the centrifugal section 21. The centrifugal impeller 34 could include full blades or a combination of full blades and splitter blades. In other embodiments, the centrifugal section 21 could include a single row or multiple rows of splitter blades. The addition of splitter blades may increase the flow capacity of the impeller 34. In a further embodiment, a diffuser 36 is arranged downstream of the impeller 34. The diffuser 36 could be a vaneless diffuser, a single row or multiple row vaned diffuser, or a pipe diffuser. A diffuser 36 may improve capacity control during various operating conditions, as well as the stable operating range of the compressor 14, which may result in higher compressor efficiency. After passing the diffuser 36, fluid F exits the compressor 14 via a volute 38, and goes on to the condenser 16. In other embodiments, a simple collector or axial exit flowpath could replace the volute 38. In some embodiments, a mixed-flow compressor could replace the centrifugal section 21 depending on design specifications. A mixed-flow compressor includes an impeller that combines axial and radial components to have a diagonal fluid flow. A mixed-flow compressor may allow for a smaller diameter shroud or casing 24.
[0036] In some embodiments, a deswirler row 39 is arranged upstream of the centrifugal section 21. The deswirler row 39 includes multiple blades and removes additional swirl flow prior to the fluid flow F entering the centrifugal section 21. In some embodiments, the compressor 14 includes an inlet guide vane 40 upstream of the axial-flow section 19. The inlet guide vane 40 may be stationary or variable. In a further embodiment, the inlet guide vane 40 is a single variable inlet guide vane. In other embodiments, the compressor 14 includes a single variable inlet guide vane 42 between the axial-flow section 19 and the centrifugal section 21. The inlet guide vane 42 may be arranged to improve system efficiency and stability by imparting either a rotational velocity component to manage the first stage incidence angle, or to expand the working fluid F to a higher specific volume, or both. Although two inlet guide vanes 40, 42 are illustrated, the compressor 14 could include more or fewer inlet guide vanes.
[0037] In a further embodiment, a flash vapor port 44 is arranged upstream of the centrifugal impeller 34. The vapor port 44 adds a small amount of flash vapor from the economizer to the flow path F, which improves refrigeration cycle efficiency.
[0038] Figure 3 illustrates another embodiment of a refrigerant compressor. In this embodiment, the vapor port 44 is arranged downstream of the deswirler row 39 and upstream of the centrifugal section 21. The illustrated embodiment does not include inlet guide vanes, but some embodiments could include inlet guide vanes upstream of the axial-flow section 19 and/or the centrifugal flow section 21.
[0039] Figure 4 illustrates another embodiment of a refrigerant compressor. In this embodiment, the compressor 14 does not include a deswirler row or inlet guide vanes.
[0040] Figure 5 illustrates another embodiment of a refrigerant compressor. In this embodiment, the compressor 14 includes a variable inlet guide vane 40 upstream of the axial- flow section 19. The vapor port 44 is arranged downstream of the deswirler row 39.
[0041] Figure 6 illustrates another embodiment of a refrigerant compressor. In this embodiment, a variable inlet guide vane 40 is arranged upstream of the axial-flow section 19, and the compressor 14 does not include a deswirler row.
[0042] Figure 7 illustrates another embodiment of a refrigerant compressor. In this embodiment, an inlet guide vane 40 is arranged upstream of the axial-flow section 19 and an inlet guide vane 42 is arranged downstream of the axial-flow section 19 but upstream of the centrifugal flow section 21. The vapor port 44 is arranged between the rotor row 28 and the stator row 30 of the axial-flow section 19.
[0043] These combinations of an axial-flow section 19 upstream of a centrifugal section 21 (or mixed-flow compressor) lead to a more compact compressor with higher shaft speeds using lower working pressure refrigerants. In some embodiments, the shaft speed is similar to shaft speeds of a conventional medium or higher working pressure refrigerant compressor. The more compact compressor additionally provides cost savings and the use of the lower working pressure refrigerant improves cycle efficiency.
[0044] It should be understood that terms such as "axial" and "radial", "centrifugal" or "mixed-flow" are used above with reference to the normal operational attitude of a compressor. Further, these terms have been used herein for purposes of explanation and should not be considered otherwise limiting. Terms such as "about" are not intended to be boundaryless terms, and should be interpreted consistent with the way one skilled in the art would interpret those terms.
[0045] Although the different examples have the specific components shown in the illustrations, embodiments of this disclosure are not limited to those particular combinations. It is possible to use some of the components or features from one of the examples in combination with features or components from another one of the examples.
[0046] One of ordinary skill in this art would understand that the above-described embodiments are exemplary and non-limiting. That is, modifications of this disclosure would come within the scope of the claims. Accordingly, the following claims should be studied to determine their true scope and content.

Claims

CLAIMS What is claimed is:
1. A refrigerant compressor, comprising
an axial section having a plurality of blades and vanes; and
a centrifugal section having an impeller downstream of the axial section.
2. The refrigerant compressor of claim 1, wherein a flash vapor port is arranged upstream of the centrifugal section.
3. The refrigerant compressor of claim 1 , wherein an inlet guide vane is arranged upstream of the axial section.
4. The refrigerant compressor of claim 3, wherein the inlet guide vane is a variable inlet guide vane.
5. The refrigerant compressor of claim 1 , wherein an inlet guide vane is arranged upstream of the centrifugal section and downstream of the axial section.
6. The refrigerant compressor of claim 5, wherein the inlet guide vane is a variable inlet guide vane.
7. The refrigerant compressor of claim 1, wherein a first inlet guide vane is arranged upstream of the axial section and a second inlet guide vane is arranged downstream of the axial section.
8. The refrigerant compressor of claim 1, further comprising a diffuser downstream of the centrifugal section.
9. The refrigerant compressor of claim 1, wherein the refrigerant compressor is part of a chiller system.
10. The refrigerant compressor of claim 1, wherein a flow path for a working fluid is defined by a hub and a casing.
11. The refrigerant compressor of claim 10, wherein the working fluid is one of HFO- 1233ZD, R123, DR-2, and HFO-1336MZZ.
12. The refrigerant compressor of claim 1, further comprising a deswirler row having a plurality of blades arranged upstream of the centrifugal section.
13. A refrigerant compressor, comprising:
an axial stage and a centrifugal stage arranged about an axis of rotation;
a fluid flowpath, wherein the fluid flowpath is substantially parallel to the axis of rotation at the axial stage, and the fluid flowpath is substantially perpendicular to the axis of rotation at the centrifugal stage.
14. The refrigerant compressor of claim 13, wherein the axial stage comprises a plurality of blades and a plurality of vanes, and the centrifugal stage comprises an impeller.
15. The refrigerant compressor of claim 13, wherein the centrifugal stage comprises a diffuser, and the fluid exits the flowpath via a volute.
16. The refrigerant compressor of claim 13, wherein the fluid is a refrigerant.
17. The refrigerant compressor of claim 16, wherein the refrigerant is one of HFO-1233ZD R123, DR-2, and HFO-1336MZZ.
18. The refrigerant compressor of claim 13, wherein a flash vapor port is arranged upstream of the centrifugal stage.
19. The refrigerant compressor of claim 13, further comprising inlet guide vanes. A refrigerant compressor, comprising
an axial section having a plurality of blades and vanes; and a mixed- flow section downstream of the axial-flow section.
PCT/US2017/042055 2016-08-25 2017-07-14 Refrigerant compressor WO2018038818A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US201662379367P true 2016-08-25 2016-08-25
US62/379,367 2016-08-25

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
US16/060,438 US10989222B2 (en) 2016-08-25 2017-07-14 Refrigerant compressor
JP2019510685A JP2019526736A (en) 2016-08-25 2017-07-14 Refrigerant compressor
CN201780049955.8A CN109952440A (en) 2016-08-25 2017-07-14 Coolant compressor
EP17844073.1A EP3504440A4 (en) 2016-08-25 2017-07-14 Refrigerant compressor
KR1020197003345A KR20190044615A (en) 2016-08-25 2017-07-14 Refrigerant compressor

Publications (1)

Publication Number Publication Date
WO2018038818A1 true WO2018038818A1 (en) 2018-03-01

Family

ID=61245207

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2017/042055 WO2018038818A1 (en) 2016-08-25 2017-07-14 Refrigerant compressor

Country Status (6)

Country Link
US (1) US10989222B2 (en)
EP (1) EP3504440A4 (en)
JP (1) JP2019526736A (en)
KR (1) KR20190044615A (en)
CN (1) CN109952440A (en)
WO (1) WO2018038818A1 (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3633202A1 (en) * 2018-10-03 2020-04-08 Danfoss A/S Hvac compressor with mixed and radial compression stages
EP3677792A1 (en) * 2019-01-02 2020-07-08 Danfoss A/S Unloading device for hvac compressor with mixed and radial compression
WO2021025851A1 (en) * 2019-08-07 2021-02-11 Carrier Corporation Axial and downstream compressor assembly
WO2021096905A1 (en) * 2019-11-13 2021-05-20 Danfoss A/S Active unloading device for mixed flow compressors

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7856834B2 (en) * 2008-02-20 2010-12-28 Trane International Inc. Centrifugal compressor assembly and method
US20160068731A1 (en) * 2013-04-16 2016-03-10 The Chemours Company Fc, Llc Methods and apparatus using refrigerant compositions comprising refrigerant and lubricant comprising perfluoropolyether and non-fluorinated lubricant

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
LU34302A1 (en)
US3941499A (en) * 1974-11-06 1976-03-02 United Turbine Ab & Co., Kommanditbolag Compressor having two or more stages
USRE32756E (en) * 1981-08-18 1988-09-27 A/S Kongsberg Vapenfabrikk Pre-swirl inlet guide vane for compressor
US6012897A (en) 1997-06-23 2000-01-11 Carrier Corporation Free rotor stabilization
US7922467B2 (en) * 2007-01-05 2011-04-12 Trane International Inc System for protecting bearings and seals of a refrigerant compressor
US7708519B2 (en) * 2007-03-26 2010-05-04 Honeywell International Inc. Vortex spoiler for delivery of cooling airflow in a turbine engine
GB0718846D0 (en) * 2007-09-27 2007-11-07 Cummins Turbo Tech Ltd Compressor
JP4951583B2 (en) * 2008-04-28 2012-06-13 日立アプライアンス株式会社 Turbo refrigerator
DE102009016392A1 (en) * 2009-04-07 2010-10-14 Man Turbo Ag compressor assembly
DE102011121925A1 (en) 2011-12-22 2013-06-27 Robert Bosch Gmbh Compressor and method for operating a compressor
ITFI20120125A1 (en) * 2012-06-19 2013-12-20 Nuovo Pignone Srl "WET GAS COMPRESSOR AND METHOD"
US9382911B2 (en) * 2013-11-14 2016-07-05 Danfoss A/S Two-stage centrifugal compressor with extended range and capacity control features
WO2015122991A2 (en) 2014-02-17 2015-08-20 Carrier Corporation Hot gas bypass for two-stage compressor
JP2016075184A (en) * 2014-10-03 2016-05-12 三菱重工業株式会社 Centrifugal compressor
CN104454568A (en) * 2014-12-12 2015-03-25 赵立军 Axial-flow type air compressor
JP6635255B2 (en) * 2015-10-26 2020-01-22 三菱重工サーマルシステムズ株式会社 Inlet guide vane, compressor, method of mounting inlet guide vane, and method of manufacturing centrifugal compressor
US20170260987A1 (en) * 2016-03-11 2017-09-14 Daikin Applied Americas Inc. Centrifugal compressor with casing treatment bypass

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7856834B2 (en) * 2008-02-20 2010-12-28 Trane International Inc. Centrifugal compressor assembly and method
US20160068731A1 (en) * 2013-04-16 2016-03-10 The Chemours Company Fc, Llc Methods and apparatus using refrigerant compositions comprising refrigerant and lubricant comprising perfluoropolyether and non-fluorinated lubricant

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
"DuPont's new HFO could replace R123", COOLING POST, 22 April 2014 (2014-04-22), XP055471938, Retrieved from the Internet <URL:http://www.coolingpost.com/world-news/duponts-new-hfo-could-replace-r123> [retrieved on 20170828] *
See also references of EP3504440A4 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3633202A1 (en) * 2018-10-03 2020-04-08 Danfoss A/S Hvac compressor with mixed and radial compression stages
EP3677792A1 (en) * 2019-01-02 2020-07-08 Danfoss A/S Unloading device for hvac compressor with mixed and radial compression
WO2021025851A1 (en) * 2019-08-07 2021-02-11 Carrier Corporation Axial and downstream compressor assembly
WO2021096905A1 (en) * 2019-11-13 2021-05-20 Danfoss A/S Active unloading device for mixed flow compressors

Also Published As

Publication number Publication date
US20200173464A1 (en) 2020-06-04
EP3504440A4 (en) 2020-04-01
US10989222B2 (en) 2021-04-27
EP3504440A1 (en) 2019-07-03
KR20190044615A (en) 2019-04-30
CN109952440A (en) 2019-06-28
JP2019526736A (en) 2019-09-19

Similar Documents

Publication Publication Date Title
US10989222B2 (en) Refrigerant compressor
JP4951583B2 (en) Turbo refrigerator
CN103620225A (en) Centrifugal compressor
KR20160084837A (en) Two-stage centrifugal compressor with extended range and capacity control features
CN101994711A (en) Centrifugal compressor and refrigerating device
WO2013112122A2 (en) Variable-speed multi-stage refrigerant centrifugal compressor with diffusers
JP2019506584A (en) Economizer used in chiller system
US20200208642A1 (en) Unloading device for hvac compressor with mixed and radial compression stages
JP6780024B2 (en) Turbo economizer used in chiller systems
US9816733B2 (en) Economizer injection assembly and method
JP2019210929A (en) Velocity type compressor and refrigeration cycle device
JP5466654B2 (en) Centrifugal compressor
WO2018127445A1 (en) Reverse cycle machine provided with a turbine
Tamaki et al. Development of High-Efficiency Centrifugal Compressor for Turbo Chiller
US11015848B2 (en) Axial flow compressor for HVAC chiller systems
US20200109879A1 (en) Hvac compressor with mixed and radial compression stages
WO2019171740A1 (en) Dynamic compressor and refrigeration cycle device
EP3434999A1 (en) Refrigeration cycle apparatus
JP2012140963A (en) Centrifugal compressor and turbo refrigerator using the same
JP2020193587A (en) Dynamic compressor, refrigeration cycle device, and method for operating dynamic compressor
US20180283736A1 (en) Low back pressure flow limiter
WO2021096905A1 (en) Active unloading device for mixed flow compressors
Brasz Increasing the Stable Operating Range of a Fixed-Geometry Variable-Speed Centrifugal Compressor
JP2014173499A (en) Centrifugal compressor and refrigerator with centrifugal compressor
WO2021071819A1 (en) Integrated connector for multi-stage compressor

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 17844073

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 20197003345

Country of ref document: KR

Kind code of ref document: A

ENP Entry into the national phase

Ref document number: 2019510685

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 2017844073

Country of ref document: EP

Effective date: 20190325